US20120208663A1 - Elements of drive power transfer belt of belt-drive continuously variable transmission for vehicle - Google Patents
Elements of drive power transfer belt of belt-drive continuously variable transmission for vehicle Download PDFInfo
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- US20120208663A1 US20120208663A1 US13/372,965 US201213372965A US2012208663A1 US 20120208663 A1 US20120208663 A1 US 20120208663A1 US 201213372965 A US201213372965 A US 201213372965A US 2012208663 A1 US2012208663 A1 US 2012208663A1
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- engagement portion
- recess
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16G—BELTS, CABLES, OR ROPES, PREDOMINANTLY USED FOR DRIVING PURPOSES; CHAINS; FITTINGS PREDOMINANTLY USED THEREFOR
- F16G5/00—V-belts, i.e. belts of tapered cross-section
- F16G5/16—V-belts, i.e. belts of tapered cross-section consisting of several parts
Definitions
- Japanese Patent Application. Publication No. 2003-247605 describes elements for addressing the problem.
- Japanese Patent Application Publication No. 2005-042803 includes some descriptions on the stress acting on the elements.
- the invention has been made, and it provides elements of a drive power transfer belt of a belt-drive continuously variable transmission for vehicles, which are less likely to exhibit undesirable behaviors and motions.
- the projection smoothly engages with the recess of the adjacent element as compared to a case where the projection is columnar having a substantially uniform diameter. Further, in a case where the projection of each element is columnar, the relative positions of the projection and the recess are radially restricted by the entirety of the projection. According to the elements of the foregoing aspect of the invention, on the other hand, the relative position of the projection is not restricted radially at the second engagement portion, that is, it is restricted only at the first engagement portion located lower than the top of the projection.
- a sheave face 20 is provided at the moveable sheave 16 b side face of the stationary sheave 16 a
- another sheave face 20 is provided at the stationary sheave 16 a side face of the moveable sheave 16 b .
- the distance, as measured in the axial direction of the first pulley 14 , between the sheave faces 20 of the first pulley 14 increases toward the radially outer side, defining a conical space between the sheaves 20 .
- the distance, as measured in the axial direction of the second pulley 16 between the sheave faces 20 of the second pulley 16 increases toward the radially outer side, defining a conical space between the sheaves 20 .
- each V-groove 12 is defined by the paired sheave faces 20 .
- first pulley 14 and the second pulley 16 correspond to “a pair of pulleys” in the invention. Further; it is to be noted that the first pulley 14 and the second pulley 16 will be collectively, or simply, referred to as “pulley” or “pulleys” where they do not need to be distinguished from each other.
- Each ring 22 is manufactured by, for example, forming a high-tension steel band, which is approximately 0.2 mm in thickness, into a loop, and then laminating nine or so of the thus formed steel bands.
- FIG. 3 is a view illustrating, by way of example, a state where the drive power transfer belt 10 is wound on the paired pulleys 14 and 16 .
- a drive pulley (drive sheave pair) PLY DR is the pulley from which drive power is transferred to the drive power transfer belt 10
- a driven pulley (driven sheave pair) PLY DVN is the pulley to which drive power is transferred from the drive power transfer belt 10 . That is, in a situation where drive power is being transferred to the drive wheels of the vehicle from the engine, the first pulley 14 serves as the drive pulley PLY DR , while the second pulley 16 serves as the driven pulley PLY DVN .
- FIG. 4 is a front view of each element 24 , as viewed in the same direction as FIG. 2 , that is, the element thickness direction DR TH .
- FIG. 5 is a right side view of the element 24 shown in FIG. 4 .
- Each element 24 is a thick platy part manufactured by, for example, punching, in a pressing process, a steel plate that is approximately 1.8 mm in thickness. That is, in the drive power transfer belt 10 , a number of the elements 24 are arranged in series along the rings 22 in the element thickness direction DR TH .
- an outer peripheral face 40 a of the first engagement portion 40 is circular as viewed in the axial direction of the projection 38
- an outer peripheral face 42 a of the second engagement portion 42 is also circular as viewed in the axial direction of the projection 38
- a top face 44 of the projection 38 is flat, or generally flat.
- a slot width W SLT which is the interval between the radially inner side inner face 46 and the radially outer side inner face 50 of the ring-fit groove 30 , is larger than a radial thickness T RG of the ring 22 .
- the projection 38 more smoothly engages with the recess 36 of the adjacent element 24 than it would do if the projection 38 was columnar having a substantially uniform diameter. Further, if the projection 38 was columnar, the relative positions of the projection 38 and the recess 36 would be radially restricted by the entirety of the projection 38 . According to the example embodiment, on the other hand, the relative position of the projection 38 is not restricted radially at the second engagement portion 42 , that is, it is restricted only at the first engagement portion 40 located lower than the top of the projection 38 .
- the width of the radial engagement gap CLC 1 is to be set to allow the elements 24 adjacent to each other to incline, as viewed in the axial direction of the pulleys 14 and 16 , relative to each other at a certain angle, rather than remaining parallel to each other, in either of the belt-riding section at the pulley 14 and that at the second pulley 16 , the width of the radial engagement gap CLC 1 can be set smaller than it would be if the projection 38 was columnar having a substantially uniform diameter.
- providing the projection 38 of each element 24 with the second engagement portion 42 is effective to sufficiently inhibit the element 24 from moving, relative to other elements 24 , upward, downward, leftward, and rightward excessively in directions parallel or substantially parallel to the first face 32 without diminishing the effect of reducing undesirable behaviors and motions of each element 24 in the belt-released sections. That is, the projections 38 of the respective elements 24 of the example embodiment provide the effect that undesirable behaviors and motions of each element 24 are suppressed in the belt-released sections, as does the projections 38 of the elements 24 ′ of the comparative example shown in FIG. 7A do.
- the side where the projections 38 of the respective elements 24 are present corresponds to the side where the belt-released section is present, while the side where the recesses 36 of the respective elements 24 are present corresponds to the side where the belt-riding section is present.
- the elements 24 are denoted “the element 24 A”, “the element 24 B”, and “the element 24 C” in this order from the belt-released section side. In the state illustrated in FIG.
- the slot gap CLC SLT (refer to the area P 09 shown in FIG. 9 ) is larger than the radial engagement gap CLC 1 .
- the distance (slide distance) over which the recess 36 and the projection 38 shown in FIGS. 6A , 6 B, and 6 C rub against each other at the drive pulley belt leaving position P 01 , the drive pulley belt entering position P 02 , the driven pulley belt entering position P 03 , and the driven pulley belt leaving position P 04 does not change even if the projection 62 shown in FIGS. 10A , 10 B, and 10 C or the projection 72 shown in FIGS. 11A , 11 B, and 11 C is provided in place of the projection 38 . That is, even in a case where the projection 38 shown in FIGS. 6A , 6 B, and 6 C is replaced with the projection 62 or the projection 72 , the same power loss reduction effect as the projection 38 shown in FIGS. 6A , 6 B, and 6 C can be obtained.
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Abstract
Description
- The disclosure of Japanese Patent Application No. 2011-029345 filed on Feb. 15, 2011 including the specification, drawings and abstract is incorporated herein by reference in its entirety.
- 1. Field of the Invention
- The invention relates to the structure of elements used as parts of a drive power transfer belt wound on a pair of pulleys used in a belt-drive continuously variable transmission for vehicles and each having a variable-width groove.
- 2. Description of Related Art
- A belt-drive continuously variable transmission is known which is provided on a power transfer path and which is constituted of a pair of pulleys each having a variable-width groove and a drive power transfer belt having a plurality of elements that are compressed at each pulley in a sandwiching manner and that are arranged in series on looped rings in the direction corresponding to the direction in which the thickness of each element is measured (will hereinafter be referred to as “element thickness direction” where necessary), the drive power transfer belt being wound on the pulleys so as to transfer power. According to such a drive power transfer belt, power is transferred between the pulleys via the drive power transfer belt with the elements pressed against each other in the element thickness direction. Therefore, if the opposed sides of the elements adjacent to each other are not sufficiently upright and parallel to each other when they are stacked on each other in the element thickness direction, an undesirable behavior or motion of each element may occur, resulting in noises and reduced efficiencies. Such a problem is described in Japanese Patent Application Publication No. 2003-247605. Further, Japanese Patent Application. Publication No. 2003-247605 describes elements for addressing the problem. Further, Japanese Patent Application Publication No. 2005-042803 includes some descriptions on the stress acting on the elements.
- The elements described in Japanese Patent Application Publication No. 2003-247605 each have a recess formed at one side of the element and a projection projecting from the other side of the element, and the projection of each element engages with the recess of the element next to it. Further, the elements described in Japanese Patent Application Publication No. 2003-247605 each have a raised portion that is slightly raised from around the projection at the other side of the element. The ratio of the length over which the raised portion is raised from the other side of the element to the thickness of the element is 0.005 or lower. According to Japanese Patent Application Publication No. 2003-247605, the structure described above ensures that the opposed sides of the elements are kept upright sufficiently.
- The projections of the respective elements described in Japanese Patent Application Publication No. 2003-247605 are generally columnar. Further, in belt-riding sections in which the drive power transfer belt wound on the pulleys are sandwiched by the respectively pulleys, the elements adjacent to each other incline relative to each other at a certain angle, as viewed in the axial direction of the pulleys, and for the purpose of allowing such relative inclinations of the elements adjacent to each other, the radial gap that is created between the projection and the recess when they are in engagement with each other is very large. For example,
FIG. 13 schematically illustrates an example case whereelements 510 are stacked on each other along the drive power transfer belt, as viewed from the radially outer side of the drive power transfer belt. In the example case illustrated inFIG. 13 , if the diameter of eachrecess 512 is D1, the diameter of eachprojection 514 is D2, and the width of the radial gap between theprojection 514 and therecess 512 is CLCD, the width of the radial gap CLCD is calculated as CLCD=D1−D2. - If the radial gap between the
projection 514 and therecess 512 is very large, for example, theelements 510 stacked on each other can not be sufficiently inhibited from moving upward, downward, leftward, and rightward in directions parallel or substantially parallel to the opposed sides of theelements 510 in the belt-riding section at one of the pulleys and the belt-riding section at the other, and this results in undesirable behaviors and motions of theelements 510. Note that “belt-riding sections” represent sections in which the drive power transfer belt rides on the respective pulleys. The “undesirable behaviors and motions” of theelements 510 include, for example, an increase in the amount of pitching motion of eachelement 510 that pitches as viewed in the axial direction of the pulleys, and an increase in the amount of yawing motion of eachelement 510 that yaws as indicated by the arrows ARyw inFIG. 13 , as viewed from the radially outer side or radially inner side of the drive power transfer belt. - When undesirable behaviors and/or motions of the
elements 510 occur in either of the belt-riding sections, for example, theelements 510 slightly rub against each other at the position from which the drive power transfer belt leaves the pulley and at the position at which the drive power transfer belt comes to ride on the pulley, and this may cause an increase in the power loss (belt loss) that the drive power transfer belt causes during the power transfer through it.FIGS. 14A and 14B are views for illustrating, as one example of “undesirable behaviors and motions” of eachelement 510, how the amount of yawing motion of eachelement 510 increases in “belt-released sections” in which the drive power transfer belt are on neither of the two pulleys. -
FIGS. 14A and 14B illustrate how the yaw angle of theelement 510 described in Japanese Patent Application Publication No. 2003-247605, which is an example of related-art elements, changes over the entire circumference of a drivepower transfer belt 516. With the drivepower transfer belt 516 shown inFIGS. 14A and 14B , the drive power is transferred from a drive pulley (drive sheave pair) 520 to a driven pulley (driven sheave pair) 518 with the stackedelements 510 being pressed against each other. The chart ofFIG. 14B shows that the more distant the value of the yaw angle is from the zero level, the larger the amount of yawing motion, regardless of which of the negative and positive sides the value of the yaw angle is in. The positions [1] to [4] at the horizontal axis of the chart inFIG. 14B correspond, respectively, to circumferential positions [1] to [4] at the drivepower transfer belt 516 shown inFIG. 14A . More specifically, the circumferential position [1] is a driven pulley belt leaving position from which the drivepower transfer belt 516 leaves the drivenpulley 518 that is rotationally driven by the drivepower transfer belt 516. The circumferential position [2] is a drive pulley belt entering position at which the drivepower transfer belt 516 comes to ride on thedrive pulley 520 that transfers drive power to the drivepower transfer belt 516. The circumferential position [3] is a drive pulley belt leaving position from which the drivepower transfer belt 516 leaves thedrive pulley 520. The circumferential position [4] is a driven pulley belt entering position at which the drivepower transfer belt 516 comes to ride on the drivenpulley 518. - Referring to
FIG. 14B , in the section from the circumferential position [3] to the circumferential position [4], the stackedelements 510 are pressed against each other for the drive power transfer. On the other hand, in the section from the circumferential position [1] to the circumferential position [2], theelements 510 are pressed against each other more lightly than they are in the section from the circumferential position (3) to the circumferential position (4), and therefore the amount of yawing motion of eachelement 510 is large in the section from the circumferential position [1] to the circumferential position [2]. In the section from the circumferential position [2] to the circumferential position [3], the yaw angle of eachelement 510 is made closer to the zero level by thedrive pulley 520. That is, the positions of therespective elements 510 are straightened in the belt-riding section at thedrive pulley 520. According to the related-art elements 510, for example, yawing motions of theelements 510 are not sufficiently restricted by the engagement between theprojection 514 and therecess 512, and therefore eachelement 510 largely yaws at the drive pulley belt entering position (i.e., the circumferential position [2]), resulting possibly in an increase in the belt loss described above. Although the example case illustrated inFIGS. 14A and 14B is mainly for explanation on yawing of theelements 510, an increase in the amount of pitching motion of eachelement 510 may possibly cause an increase in the belt loss, etc. - It is to be noted that such problems have never been addressed in public.
- In view of the above, the invention has been made, and it provides elements of a drive power transfer belt of a belt-drive continuously variable transmission for vehicles, which are less likely to exhibit undesirable behaviors and motions.
- An aspect of the invention relates to a set of elements that are arranged, in an element thickness direction, in series along a looped ring of a drive power transfer belt wound on a pair of pulleys of a belt-drive continuously variable transmission. Each of the elements has a recess that is provided at one side of the element and a projection projecting from the other side of the element to fit into the recess of the adjacent element. The projection has a first engagement portion that is provided at a base side of the projection such that a predetermined engagement gap is created on a radially outer side of the first engagement portion when the projection fits in the recess of the adjacent element, and a second engagement portion which is provided at a tip side of the projection and that, at least partially, decreases in diameter thereof toward a tip of the projection from the first engagement portion, wherein a gradient with which the diameter of the second engagement portion decreases toward the tip of the projection is larger than a gradient with which a diameter of the first engagement portion decreases toward the tip of the projection.
- According to the set of elements structured as described above, owing to the second engagement portion provided at the tip side of the projection, the projection smoothly engages with the recess of the adjacent element as compared to a case where the projection is columnar having a substantially uniform diameter. Further, in a case where the projection of each element is columnar, the relative positions of the projection and the recess are radially restricted by the entirety of the projection. According to the elements of the foregoing aspect of the invention, on the other hand, the relative position of the projection is not restricted radially at the second engagement portion, that is, it is restricted only at the first engagement portion located lower than the top of the projection. Therefore, in a case where the width of the predetermined engagement gap is to be set to allow the elements adjacent to each other to incline, as viewed in the axial direction of the pulleys, relative to each other at a certain angle, rather than remaining parallel to each other, in the belt-riding sections, the width of the predetermined engagement gap can be set smaller than the radial gap that would be created between the projection and the recess if the projection was columnar having a substantially uniform diameter. As a result, each element is sufficiently restricted so as not to move upward, downward, leftward, and rightward excessively in directions parallel or substantially parallel to the opposed sides of the respective elements in the belt-released sections, and undesirable behaviors and motions of each element are more effectively suppressed by the engagement between the projection and the recess than they would be if the projection of each element was columnar. As a result, for example, the power loss (belt loss) is reduced.
- Further, the set of elements of the foregoing aspect of the invention may be such that: each of the elements has a ring-fit groove in which the ring is fit; and a gap that is created in a radial direction of the pulley between a radially outer side inner face of the ring-fit groove and an outer peripheral face of the ring when a radially inner side inner face of the ring-fit groove is in contact with an inner peripheral face of the ring is larger than the predetermined engagement gap. Each element is moved toward the radially outer side of the drive power transfer belt by the recess of the preceding adjacent element and the ring at the moment the element leaves each pulley. According to the above-described structure, the work of the recess of the preceding adjacent element in the above state is large, and therefore the pressing force that the element applies, when moved toward the radially outer side of the drive power transfer belt, to the ring is small, resulting in a longer life of the ring, that is, a longer life of the drive power transfer belt.
- Further, the set of elements of the foregoing aspect of the invention may be such that an inclined face of which a gradient with respect to an axis of the projection is larger than a gradient of the first engagement portion with respect to the axis of the projection is provided at least at a portion, at a side corresponding to a radially outer side of the drive power transfer belt, of the second engagement portion. According to this structure, the gap between the tip of the projection and the recess is sufficiently large at the side corresponding to the radially outer side of the drive power transfer belt. As such, when the adjacent elements incline relative to each other at a certain angle, as viewed in the axial direction of the pulleys, in the belt-riding sections at the respective pulleys, each projection is more unlikely to interfere with or contact the recess into which the same projection fits. It is to be understood that the inclined face of which the gradient with respect to the axis of the projection is larger than the gradient of the first engagement portion with respect to the same axis may be provided only at the portion, at the side corresponding to the radially outer side of the drive power transfer belt, of the second engagement portion.
- Further, the set of elements of the foregoing aspect of the invention may be such that a height of the first engagement portion from the other side of the element is within a range of 0.25 to 0.4 mm. According to this structure, undesirable behaviors and motions of each element in the belt-released sections can be more effectively suppressed, and further the distance over which the outer peripheral face of the projection and the inner peripheral face of the recess rub against each other when the projection and the recess slide on each other in the longitudinal, direction of the drive power transfer belt at the drive pulley belt leaving position, the drive pulley belt entering position, the driven pulley belt entering position, and the driven pulley belt leaving position is reduced, resulting in a smaller power loss that is caused by the outer peripheral face of the projection and the inner peripheral face of the recess rubbing against each other. It is to be noted that “the drive pulley belt leaving position” is the position from the drive power transfer belt leaves the drive pulley, “the drive pulley belt entering position” is the position at which the drive power transfer belt comes to ride on the drive pulley, “the driven pulley belt entering position” is the position at which the drive power transfer belt comes to ride on the driven pulley, and “the driven pulley belt leaving position” is the position from which the drive power transfer belt leaves the driven pulley. For example, if the height of the first engagement portion is smaller than 0.25 mm, there arises a possibility of insufficient engagement between the first engagement portion and the recess in a state where the projection of one element fits in the recess of the element adjacent to it, and this may result in a failure to suppress undesirable behaviors and motions of the elements sufficiently in the belt-released sections. On the other hand, if the height of the first engagement portion is larger than 0.4 mm, there arises a possibility of an excessive increase in the distance over which the outer peripheral face of the projection and the inner peripheral face of the recess rub against each other, and this may result in an increase in the power loss (belt loss).
- Further, the set of elements of the foregoing aspect of the invention may be such that an outer peripheral face of the second engagement portion includes a portion formed by rounding a peripheral edge of a top face of the projection at a curvature radius of 0.4 to 0.5 mm. According to this structure, undesirable behaviors and motions of the elements at each belt-released section can be more properly suppressed. Further, the distance over which the outer peripheral face of the projection and the inner peripheral face of the recess rub against each other when the projection and the recess slide on each other in the longitudinal direction of the drive power transfer belt at the drive pulley belt leaving position, the drive pulley belt entering position, the driven pulley belt entering position, and the driven pulley belt leaving position is reduced, resulting in a smaller power loss that is caused by the outer peripheral face of the projection and the inner peripheral face of the recess rubbing against each other. For example, if the curvature radius is larger than 0.5 mm, there arises a possibility of insufficient engagement between the first engagement portion and the recess in a state where the projection of one element fits in the recess of the element adjacent to it, and this may result in a failure to suppress undesirable behaviors and motions of the elements sufficiently in the belt-released sections. On the other hand, if the curvature radius is smaller than 0.4 mm, there arises a possibility of an excessive increase in the distance over which the outer peripheral face of the projection and the inner peripheral face of the recess rub against each other, and this may result in an increase in the power loss.
- Further, the set of elements of the foregoing aspect of the invention may be such that the diameter of the projection decreases toward the tip of the projection from the other side of the element, and the element having said projection is located on an inner side of an arc that is drawn about a rocking center about which said element rocks relative to the element adjacent to said element, as viewed in an axial direction of the pulleys, such that the arc runs through a position at a base of said projection, the position being most distant from the rocking center. According to this structure, for example, when the projection slides, in the longitudinal direction of the drive power transfer belt, into the recess mating with it as the element having the same projection rocks about the rocking center at the drive pulley belt leaving position, the drive pulley belt entering position, the driven pulley belt entering position, or the driven pulley belt leaving position, the rubbing between the outer peripheral face of the projection and the inner peripheral face of the recess can be reduced, resulting in a decrease in the power loss that is caused by such rubbing.
- The features, advantages, and technical and industrial significance of this invention will be described in the following detailed description of example embodiments of the invention with reference to the accompanying drawings, in which like numerals denote like elements, and wherein:
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FIG. 1 is a perspective view illustrating a state where a drive power transfer belt to which the invention is applied is set in a belt-drive continuously variable transmission for vehicles; -
FIG. 2 is a sectional view taken along the plane indicated by the arrow II inFIG. 1 , showing cross sections of the drive power transfer belt and its periphery; -
FIG. 3 is a view illustrating a state where the drive power transfer belt is wound on the paired pulleys of the continuously variable transmission shown inFIG. 1 ; -
FIG. 4 is a front view of each element of the example embodiment of the invention, as seen in the element thickness direction; -
FIG. 5 is a right side view of the element shown inFIG. 4 ; -
FIG. 6A is an enlarged view of the projection and its periphery shown in the front view ofFIG. 4 ; -
FIG. 6B is a sectional view of the projection, which is taken along the line indicated by the arrows B1 inFIG. 6A ; -
FIG. 6C is a sectional view of the projection, which is taken along the line indicated by the arrows C1 inFIG. 6A , which is orthogonal to the line indicated by the arrows B1 inFIG. 6A ; -
FIG. 7A is a view showing elements, each having a projection with an outer peripheral face uniformly tapered, of a comparative example for a comparison with the elements of the example embodiment of the invention; -
FIG. 7B is a view illustrating, by way of example, how the projection of one element fits in the recess of other element when the multiple elements are stacked on each other in either of the belt-released sections shown inFIG. 3 and how undesirable behaviors and motions of the elements are suppressed; -
FIG. 8A is a view illustrating, by way of example, how a power loss occurs with related-art elements, for a comparison with the example embodiment in which such a power loss is reduced effectively; -
FIG. 8B is a view illustrating, by way of example, how the inner peripheral face of the recess of one of the elements of the example embodiment and the outer peripheral face of the projection of the element adjacent to it rub against each other, and illustrating, by way of example, how a power loss caused by the drive power transfer belt is reduced; -
FIG. 9 is an enlarged view of the recess, the ring, and their peripheries at the drive pulley belt leaving position P01 or at the driven pulley belt leaving position P04 shown inFIG. 3 , illustrating, by way of example, how each element is moved toward the radially outer side of the drive power transfer belt at the drive pulley belt leaving position P01 and at the driven pulley belt leaving position P04; -
FIG. 10A is an enlarged view of a projection of an element as the first modification example of the example embodiment of the invention shown inFIGS. 6A , 6B, and 6C, and its periphery, showing the detailed form of the same projection; -
FIG. 10B is a sectional view of the projection taken along the line indicated by the arrows B2 inFIG. 10A ; -
FIG. 10C is a sectional view of the projection taken along the line indicated by the arrows C2 inFIG. 10A , which is orthogonal to the line indicated by the arrows B2; -
FIG. 11A is an enlarged view of a projection of an element as the second modification example of the example embodiment of the invention shown inFIGS. 6A , 6B, and 6C, and its periphery, showing the detailed form of the same projection; -
FIG. 11B is a sectional view of the projection taken along the line indicated by the arrows B3 inFIG. 11A ; -
FIG. 11C is a sectional view of the projection taken along the line indicated by the arrows C3 inFIG. 11A , which is orthogonal to the line indicated by the arrows B3; -
FIG. 12A is an enlarged view of a projection of an element as the third modification example of the example embodiment of the invention shown inFIGS. 6A , 6B, and 6C, and its periphery, showing the detailed form of the same projection; -
FIG. 12B is a sectional view of the projection taken along the line indicated by the arrows B4 inFIG. 12A ; -
FIG. 12C is a sectional view of the projection taken along the line indicated by the arrows C4 inFIG. 12A , which is orthogonal to the line indicated by the arrows B4; -
FIG. 13 is a view schematically illustrating an example case where elements are stacked on each other along the drive power transfer belt, as seen from the radially outer side of the drive power transfer belt, which is used for explaining, by way of example, a problem that the invention solves; -
FIG. 14A is a simplified view illustrating the positional relation between a drive pulley, a driven pulley, and a drive power transfer belt of a related-art continuously variable transmission; and -
FIG. 14B is a view illustrating how the yaw angle of a related-art element changes over the entire circumference of a drive power transfer belt, which is used for explaining, by way of example, a problem that the invention solves. - Hereinafter, en example embodiment of the invention will be described in detail with reference to the drawings.
FIG. 1 is a perspective view illustrating, by way of example, a state where a drivepower transfer belt 10 to which the invention is applied is set in a vehicle belt-drive continuously variable transmission 8 (will hereinafter be referred to as “the belt-drive continuously variable transmission 8”).FIG. 2 is a sectional view taken along the plane indicated by the arrow II inFIG. 1 , showing cross sections of the drivepower transfer belt 10 and its periphery. Referring toFIGS. 1 and 2 , the drivepower transfer belt 10 is a compression type drive power transfer belt (metallic belt) that is wound on afirst pulley 14 and asecond pulley 16 that are rotatable, respectively, about two parallel axes and that each have a V-groove 12 which is provided at the radially outer side of the pulley and of which the width is variable. The first pulley (first sheave pair) 14 is an input pulley to which the drive power of an engine, which is the drive power source of the vehicle, is input, and the second pulley (second sheave pair) 16 is an output pulley from which the drive power is output to the drive wheels of the vehicle. Thefirst pulley 14 is constituted of astationary sheave 14 a fixed on arotational shaft 18 and amoveable sheave 14 b provided on therotational shaft 18 such that it is axially moveable relative to therotational shaft 18. Likewise, thesecond pulley 16 is constituted of astationary sheave 16 a fixed on anotherrotational shaft 18 and amoveable sheave 16 b provided on therotational shaft 18 such that it is axially moveable relative to therotational shaft 18. Asheave face 20 is provided at themoveable sheave 14 b side face of thestationary sheave 14 a, and anothersheave face 20 is provided at thestationary sheave 14 a side face of themoveable sheave 14 b. Likewise, asheave face 20 is provided at themoveable sheave 16 b side face of thestationary sheave 16 a, and anothersheave face 20 is provided at thestationary sheave 16 a side face of themoveable sheave 16 b. The distance, as measured in the axial direction of thefirst pulley 14, between the sheave faces 20 of thefirst pulley 14 increases toward the radially outer side, defining a conical space between thesheaves 20. Likewise, the distance, as measured in the axial direction of thesecond pulley 16, between the sheave faces 20 of thesecond pulley 16 increases toward the radially outer side, defining a conical space between thesheaves 20. That is, each V-groove 12 is defined by the paired sheave faces 20. It is to be noted that thefirst pulley 14 and thesecond pulley 16 correspond to “a pair of pulleys” in the invention. Further; it is to be noted that thefirst pulley 14 and thesecond pulley 16 will be collectively, or simply, referred to as “pulley” or “pulleys” where they do not need to be distinguished from each other. - The drive
power transfer belt 10 is provided with a pair ofrings 22 each constituted of multiple looped flexible steel bands stacked on top of each other, and a plurality ofelements 24 that are thin metal members supported by therings 22 and stacked into a loop along therings 22 in the direction indicated by the arrow DRTH inFIG. 5 . Note that the direction DRTH is the direction in which the thickness of eachelement 24 is measured and thus it will hereinafter be referred to as “the element thickness direction DRTH”. - Each
ring 22 is manufactured by, for example, forming a high-tension steel band, which is approximately 0.2 mm in thickness, into a loop, and then laminating nine or so of the thus formed steel bands. -
FIG. 3 is a view illustrating, by way of example, a state where the drivepower transfer belt 10 is wound on the paired pulleys 14 and 16. InFIG. 3 , a drive pulley (drive sheave pair) PLYDR is the pulley from which drive power is transferred to the drivepower transfer belt 10, while a driven pulley (driven sheave pair) PLYDVN is the pulley to which drive power is transferred from the drivepower transfer belt 10. That is, in a situation where drive power is being transferred to the drive wheels of the vehicle from the engine, thefirst pulley 14 serves as the drive pulley PLYDR, while thesecond pulley 16 serves as the driven pulley PLYDVN. On the other hand, in a situation where drive power is being transferred to the engine from the drive wheels of the vehicle, such as during engine brake, thesecond pulley 16 serves as the drive pulley PLYDR, while thefirst pulley 14 serves as the driven pulley PLYDVN. In the example case illustrated inFIG. 3 , thefirst pulley 14 is the drive pulley PLYDR, and thesecond pulley 16 is the driven pulley PLYDVN. Referring toFIG. 3 , the sections in which theelements 24 of the drivepower transfer belt 10 ride on the respectively pulleys 14 and 16 will hereinafter be referred to as “belt-riding sections” where necessary, and the sections between the two belt-riding sections (i.e., the sections in which theelements 24 of the drivepower transfer belt 10 are on neither of thepulleys 14 and 16) will hereinafter be referred to as “belt-released sections” where necessary. - When the drive pulley PLYDR rotates to propel the drive
power transfer belt 10 as indicated by the arrow ARDR inFIG. 3 , a position P01 at the drive pulley PLYDR is a drive pulley belt leaving position from the drivepower transfer belt 10 leaves the drive pulley PLYDR, a position P02 at the drive pulley PLYDR is a drive pulley belt entering position at which the drivepower transfer belt 10 comes to ride on the drive pulley PLYDR, a position P03 at the driven pulley PLYDVN is a driven pulley belt entering position at which the drivepower transfer belt 10 comes to ride on the driven pulley PLYDVN, and a position P04 at the driven pulley PLYDVN is a driven pulley belt leaving position from which the drivepower transfer belt 10 leaves the driven pulley PLYDVN. In the example case illustrated inFIG. 3 , since the drivepower transfer belt 10 is running in the direction indicated by the arrow ARDR, the drive power is transferred to the driven pulley PLYDVN from the drive pulley PLYDR with theelements 24 pressed against each other in the belt-released section between the drive pulley belt leaving position P01 to the driven pulley belt entering position P03. -
FIG. 4 is a front view of eachelement 24, as viewed in the same direction asFIG. 2 , that is, the element thickness direction DRTH.FIG. 5 is a right side view of theelement 24 shown inFIG. 4 . Eachelement 24 is a thick platy part manufactured by, for example, punching, in a pressing process, a steel plate that is approximately 1.8 mm in thickness. That is, in the drivepower transfer belt 10, a number of theelements 24 are arranged in series along therings 22 in the element thickness direction DRTH. - Referring to
FIGS. 2 , 4, and 5, eachelement 24 has a pair of contact faces 26, a rockingedge portion 28, a pair of ring-fit grooves 30, afirst face 32, asecond face 34, and a recess (hole) 36, and aprojection 38. The two contract faces 26 are opposed to and in contact with the respective sheave faces 20. The rockingedge portion 28 extends straight, or substantially straight, in the axial direction of thepulleys fit grooves 3 are grooves in which therespective rings 22 are fit and which restrict therespective rings 22 radially with respect to theelements 24. Thefirst face 32 is one of faces in the element thickness direction DRTH, while thesecond face 34 is the other. The recess (hole) 36 is provided in thefirst face 32 at a position that is on the radially outer side of the rockingedge portion 28 with respect to the drivepower transfer belt 10. Theprojection 38 projects from thesecond face 34 so as to fit into therecess 36 of theadjacent element 24. - The rocking
edge portion 28 serves as the center about which theelement 24 rocks relative to theadjacent element 24, as viewed in the axial direction of thepulleys element 24 contacts theadjacent element 24 in each belt-riding section in which the drivepower transfer belt 10 bends. - The
second face 34 of eachelement 24 is parallel, or substantially parallel to thefirst face 32 of thesame element 24. In a state where theelements 24 are stacked on each other in the element thickness direction DRTH, thesecond face 34 of eachelement 24 is opposed to thefirst face 32 of theelement 24 adjacent to it. - The
recess 36 of eachelement 24 is a dent formed by, for example, pressing thefirst face 32. The axis of therecess 36 is perpendicular to thefirst face 32, and the inner peripheral face of therecess 36 is circular as viewed in the axial direction of therecess 36. Therecess 36 is formed such that a radial gap having a predetermined width and an axial gap having a predetermined width are created between therecess 36 and theprojection 38 of theadjacent element 24 when thesame projection 38 fit in therecess 36. -
FIGS. 6A , 613, and 6C are views showing the detailed form of theprojection 38 of eachelement 24. More specifically,FIG. 6A is an enlarged view of theprojection 38 and its periphery, as viewed in the same direction inFIG. 4 (refer to the area V1 inFIG. 4 ).FIG. 6B is a sectional view of theprojection 38, which is taken along the line indicated by the arrows B1 inFIG. 6A .FIG. 6C is a sectional view of theprojection 38, which is taken along the line indicated by the arrows C1 inFIG. 6A , which is orthogonal to the line indicated by the arrows B1. Theprojection 38 of eachelement 24 is formed, for example, as a result of forming therecess 36 by pressing. That is, as therecess 36 is formed by pressing, theprojection 38 is upraised perpendicularly from thesecond face 34. In this example embodiment of the invention, therecess 36 and theprojection 38 of eachelement 24 are coaxial. The height of theprojection 38 from thesecond face 34, which will hereinafter be referred to as “projection height” where necessary) is, for example, 0.75 to 0.8 mm. Referring toFIG. 6B , theprojection 38 has afirst engagement portion 40 provided at the base side of theprojection 38 and asecond engagement portion 42 provided at the tip side of theprojection 38. Referring toFIG. 6C , an outerperipheral face 40 a of thefirst engagement portion 40 is circular as viewed in the axial direction of theprojection 38, and an outerperipheral face 42 a of thesecond engagement portion 42 is also circular as viewed in the axial direction of theprojection 38. Atop face 44 of theprojection 38 is flat, or generally flat. - The
first engagement portion 40, which a portion of theprojection 38 as described above, serves to restrict, radially, the position of theprojection 38 relative to the position of therecess 36 in which theprojection 38 fits. Thefirst engagement portion 40 may be formed in a columnar shape of which the diameter is uniform. In this example embodiment, however; the outerperipheral face 40 a of thefirst engagement portion 40 is tapered at a tapering angle corresponding to the draft angle for the pressing described above, so that the diameter of theprojection 38 decreases toward its tip. Thefirst engagement portion 40 is formed such that a radial engagement gap CLC1 having a predetermined width is created between thefirst engagement portion 40 of theprojection 38 and therecess 36 of theadjacent element 36 when theprojection 38 fits in therecess 36. More specifically, the radial engagement gap CLC1 is created between therecess 36 and thefirst engagement portion 40 of theprojection 38 when theprojection 38 and therecess 36 of theadjacent element 24 are in engagement with each other, and at least the portion, which is opposed to the outerperipheral face 40 a of the first engagement portion in this state, of the inner peripheral face of therecess 36 is tapered at the same tapering angle as the outerperipheral face 40 a of thefirst engagement portion 40. The width of the radial engagement gap CLC1 is calculated as the difference between the diameter of therecess 36 and that of thefirst engagement portion 40. Referring toFIG. 5 , if the diameter of thefirst engagement portion 40 measured when theprojection 38 is in a predetermined position along the axial direction of theprojection 38 and in engagement with therecess 36 is DN and the diameter of therecess 36 measured when therecess 36 is in a predetermined position along the axial direction of therecess 36 and in engagement of theprojection 38 is DH, the width of the radial engagement gap CLC1 is calculated as DH−DN. More specifically, the diameter DN of thefirst engagement portion 40 is the diameter of thefirst engagement portion 40 measured at its base, and the diameter DH of therecess 36 is the diameter of therecess 36 measured at its opening. The width of the radial engagement gap CLC1 is, for example, empirically set to a value that does not inhibit nor hinder theelements 24 in engagement from rocking properly about theirrocking edge portions 28, respectively, in the element thickness direction DRTH when thesame elements 24 are in either of the belt-riding sections shown inFIG. 3 and that sufficiently suppresses undesirable behaviors and motions, such as pitching and yawing, of theelements 24 when they are at the drive pulley belt leaving position P01 of the drive pulley PLYBR or at the drive pulley belt entering position P02 of the drive pulley PLYDR (refer toFIG. 3 ) and when they are at the driven pulley belt entering position P03 of the driven pulley PLYDVN or at the driven pulley belt leaving position P04 of the driven pulley PLYDVN (refer toFIG. 3 ). The height of thefirst engagement portion 40 from thesecond face 34 is not limited to any specifically value. However, preferably, it is set within the range of 0.25 to 0.4 mm. This range of the height of thefirst engagement portion 40 has been empirically set as a range that ensures that thefirst engagement portion 40 of theprojection 38 and therecess 36 engage enough to suppress undesirable behaviors and motions of theelements 24 when they are stacked on each other in either of the belt-released sections described above, and that minimizes the power loss caused by the outerperipheral face 40 a of thefirst engagement portion 40 and the inner peripheral face of therecess 36 rubbing against each other at the drive pulley belt leaving position P01, the drive pulley belt entering position P02, the driven pulley belt entering position P03, and the driven pulley belt leaving position P04 (refer toFIG. 3 ). - Next, the
second engagement portion 42 extending from thefirst engagement portion 40 toward to the tip of theprojection 38 is adapted to ensure that theprojection 38 smoothly fits into therecess 36 of theadjacent element 24. More specifically, referring toFIGS. 6A , 6B, and 6C, thesecond engagement portion 42 is formed such that its diameter decreases toward to the tip of theprojection 38 from the upper end of thefirst engagement portion 40. Further, the diameter decrease gradient with respect to the direction from the base to the tip of theprojection 38 is larger at thesecond engagement portion 42 than at thefirst engagement portion 40. That is, the tapering angle of the outerperipheral face 42 a of thesecond engagement portion 42 is larger than that of the outerperipheral face 40 a of thefirst engagement portion 40. The width of the radial gap that is created between therecess 36 and thesecond engagement portion 42 when therecess 36 and thesecond engagement portion 42 are in engagement with each other is equal to or larger than the width of the radial engagement gap. CLC1 (preferably larger than the width of the radial engagement gap CLC1). That is, the width of the radial engagement gap CLC1 is the minimum width of the radial gap between therecess 36 and theprojection 38 when therecess 36 and theprojection 38 are in engagement with each other. In other words, the radial engagement gap CLC1 is the minimum radial gap between therecess 36 and theprojection 38. - Referring to
FIG. 4 , as viewed in the element thickness direction DRTH, the ring-fit grooves 30 of eachelement 24 are rectangular, extending outward in the axial direction of thepulleys power transfer belt 10, a radially inner sideinner face 46 of the ring-fit groove 30 and an innerperipheral face 48 of thering 22 are opposed to each other, while a radially outer sideinner face 50 of the ring-fit groove 30 and an outerperipheral face 52 of thering 22 are opposed to each other. Further, a slot width WSLT, which is the interval between the radially inner sideinner face 46 and the radially outer sideinner face 50 of the ring-fit groove 30, is larger than a radial thickness TRG of thering 22. Further, the width of a slot gap CLCSLT(=WSLT−TRG), which is the gap that is created, on the radially outer side of thering 22, between the radially outer sideinner face 50 of the ring-fit groove 30 and the outerperipheral face 52 of thering 22 when the radially inner sideinner face 46 of the ring-fit groove 30 and the innerperipheral face 48 of thering 22 are in contact with each other, is empirically set as follows. For example, the width of the slot gap CLCSLT is empirically set to a value that does not inhibit nor hinder theelement 24 from rocking about the rockingedge portion 28 while the drivepower transfer belt 10 is running and that ensures smooth engagement between therecess 36 and theprojection 38 at theelements 24 stacked on each other. The slot gap CLCSLT is larger than the radial engagement gap CLC1. - According to the example embodiment, the
projection 38 of eachelement 24 has thefirst engagement portion 40 that is provided at the base side of theprojection 38 such that, when theprojection 38 fits in therecess 36 of theadjacent element 24, the radial engagement gap CLC1 is created between thefirst engagement portion 40 and therecess 36. Further, theprojection 38 of eachelement 24 has thesecond engagement portion 42 that is provided at the tip side of theprojection 38 and decreases in diameter toward the tip of theprojection 38 from the upper end of thefirst engagement portion 40 with a gradient, with respect to the direction from the base to the tip of theprojection 38, being larger than the gradient with which thefirst engagement portion 40 decreases in the same direction. As such, owing to thesecond engagement portion 42 provided at the tip side of theprojection 38, theprojection 38 more smoothly engages with therecess 36 of theadjacent element 24 than it would do if theprojection 38 was columnar having a substantially uniform diameter. Further, if theprojection 38 was columnar, the relative positions of theprojection 38 and therecess 36 would be radially restricted by the entirety of theprojection 38. According to the example embodiment, on the other hand, the relative position of theprojection 38 is not restricted radially at thesecond engagement portion 42, that is, it is restricted only at thefirst engagement portion 40 located lower than the top of theprojection 38. Therefore, in a case where the width of the radial engagement gap CLC1 is to be set to allow theelements 24 adjacent to each other to incline, as viewed in the axial direction of thepulleys pulley 14 and that at thesecond pulley 16, the width of the radial engagement gap CLC1 can be set smaller than it would be if theprojection 38 was columnar having a substantially uniform diameter. As a result, eachelement 24 is sufficiently restricted so as not to move, relative toother elements 24, upward, downward, leftward, and rightward excessively in directions parallel, or substantially parallel to thefirst face 32, when theelement 24 is in either of the belt-released sections, and undesirable behaviors and motions of eachelement 24 are more effectively suppressed by the engagement between theprojection 38 and therecess 36 than they would be if theprojection 38 of eachelement 24 was columnar having a substantially uniform diameter. As a result, for example, the power loss (belt loss) that may be caused by undesirable behaviors and motions of theelements 24 in the respective belt-released sections is reduced. Further, a decrease in the contact area between the sheave faces 20 which may be caused by undesirable behaviors and motions of eachelement 24 can be minimized, and wear of the sheave faces 20 which may occur as the positions of therespective elements 24 are straightened in the belt-riding sections in therespective pulleys 14 and 16 (refer toFIG. 3 ) can minimized. Further, owing to thesecond engagement portion 42 provided at the tip side of theprojection 38 of eachelement 24, the distance (slide distance) over which the inner peripheral face of therecess 36 and the outer peripheral face of theprojection 38 rub against each other as theelement 24 rocks about the rockingedge portion 28 is shorter than it would be if the entire outer peripheral face of theprojection 38 was tapered at an angle that is equal to or substantially equal to the tapering angle of thefirst engagement portion 40 described above, and therefore the power loss due to the rubbing (slippage) between the inner peripheral face of therecess 36 and the outer peripheral face of theprojection 38 is small. In the following, the effects of the reduced undesirable behaviors and motions of theelements 24 and the reduced power losses will be described in more detail with reference toFIGS. 7A , 7B andFIGS. 8A and 8B , respectively. -
FIG. 7A is a view illustrating, by way of example, how theprojection 38 of oneelement 24′ of a comparative example fits in therecess 36 ofother element 24′ when theelements 24′ are stacked on each other in either of the belt-released section between the drive pulley belt leaving position P01 and the driven pulley belt entering position P03 and the belt-released section between the driven pulley belt leaving position P04 and the drive pulley belt entering position P02. Note that theprojection 38 of eachelement 24′ of the comparative example shown inFIG. 7A does not have any portion corresponding to thesecond engagement portion 42, that is, the outer peripheral face of theprojection 38 is uniformly tapered. In contrast,FIG. 7B is a view illustrating, by way of example, how theprojection 38 of oneelement 24 of the example embodiment fits in therecess 36 ofother element 24 when theelements 24 of the example embodiment are stacked on each other in either of the belt-released section between the drive pulley belt leaving position P01 and the driven pulley belt entering position P03 and the belt-released section between the driven pulley belt leaving position P04 and the drive pulley belt entering position P02.FIG. 7A is a sectional view longitudinally taken along the axes of theprojections 38 of therespective elements 24′ of the comparative example.FIG. 7B is a sectional view longitudinally taken along the axes of theprojections 38 of therespective elements 24 of the example embodiment. It is to be noted that the sectional views 7A and 73 shows the same side of the element as the side of the element shown byFIG. 5 . In the following, how undesirable behaviors and motions of eachelement 24 of the example embodiment are suppressed will be described, by way of example, with reference toFIGS. 7A and 7B . Referring toFIG. 7B , in the example embodiment, the width of the radial gap between the inner peripheral face of therecess 36 and the outerperipheral face 40 a of thefirst engagement portion 40 of the projection 38 (refer to the area P06 shown inFIG. 7B ) is minimum (i.e., the radial engagement gap CLC1) when theelements 24 are in either of the belt-released sections described above, and the width of the same minimum gap is equal to or substantially equal to the width of the radial gap that is created between the inner peripheral face of therecess 36 and the outer peripheral face of the projection 38 (refer to the area P05 shown inFIG. 7A ) when theelements 24′ of the comparative example are in either of the belt-released sections described above. As such, providing theprojection 38 of eachelement 24 with thesecond engagement portion 42 is effective to sufficiently inhibit theelement 24 from moving, relative toother elements 24, upward, downward, leftward, and rightward excessively in directions parallel or substantially parallel to thefirst face 32 without diminishing the effect of reducing undesirable behaviors and motions of eachelement 24 in the belt-released sections. That is, theprojections 38 of therespective elements 24 of the example embodiment provide the effect that undesirable behaviors and motions of eachelement 24 are suppressed in the belt-released sections, as does theprojections 38 of theelements 24′ of the comparative example shown inFIG. 7A do. That is, in the example embodiment, since undesirable behaviors and motions of eachelement 24 are suppressed in the belt-released sections due to the engagement gap CLC1 created as described above, eachelement 24 is in a good position when reaching the drive pulley belt entering position P02 and when reaching the driven pulley bell entering position P03. -
FIG. 8A is a view illustrating, by way of example, how the inner peripheral face of therecess 36 of one of theelements 24′ of the comparative example and the outer peripheral face of theprojection 38 of theelement 24′ adjacent to it rub against each other.FIG. 8B is a view illustrating, by way of example, how the inner peripheral face of therecess 36 of one of theelements 24 of the example embodiment and the outer peripheral face of theprojection 38 of theelement 24 adjacent to it rub against each other. In the following, how the power loss can be reduced in the example embodiment of the invention will be described, by way of example, with reference toFIGS. 8A and 8B . It is to be noted thatFIGS. 8A and 8B are longitudinal sectional views, likeFIGS. 7A and 7B , and theelements 24′ shown inFIG. 8A correspond to theelements 24′ of the comparative example shown inFIG. 7A , while theelements 24 shown inFIG. 8B correspond to theelements 24 of the example embodiment shown inFIG. 7B . At the drive pulley belt leaving position P01, the drive pulley belt entering position P02, the driven pulley belt entering position P03, and the driven pulley belt leaving position P04 (refer toFIG. 3 ) at which each element 24 (24′) shifts from the belt-riding section to the belt-released section or vice versa, the motion of each element 24 (24′) shifts from a curvilinear motion (i.e., the motion in each belt-riding section) to a linear motion (i.e., the motion in each belt-released section) or vice versa, and therefore the curvature radius of the drive power transfer belt 10 (i.e., each portion of the drivepower transfer belt 10 entering or leaving the pulley) changes, causing the stacked elements 24 (24′) to rock about theirrocking edge portions 28, respectively, as shown inFIGS. 8A and 8B . In this state, the inner peripheral face of therecess 36 and the outer peripheral face of theprojection 38 slide, in the longitudinal direction of the drivepower transfer belt 10, on each other at the side corresponding to the radially outer side of the drivepower transfer belt 10, and at this time, the stacked elements 24 (24′) are pressed against each other, producing compressing force compressing each element 24 (24′) in the element thickness direction DRTH. In this way, a power loss (belt loss) is caused by the sliding of therecess 36 and theprojection 38. If such a power loss is denoted “LSSBLT”, it is calculated by the following equation (1). Note that the unit of the power loss LSSBLT is W, for example. -
LSS BLT =μ×Q×sin β×LH×((Din×/t)×(Nin/60))×2 (1) - In the equation (1) above, μ is the friction coefficient between the inner peripheral face of the
recess 36 and the outer peripheral face of theprojection 38. Q represents the compression force acting, on the element 24 (24′) in the element thickness direction DRTH as described above. β represents the inclination angle (hole angle) of the inner peripheral face of the recess (hole) 36 relative to its axis. LH represents the distance over which therecess 36 and theprojection 38 slide on each other. In the comparative example illustrated inFIG. 8A , the slide distance LH is a length L24′ of the liner portion of the outer peripheral face of the projection of theelement 24′ as viewed in the longitudinal sectional view. In the example embodiment illustrated inFIG. 8B , on the other hand, the slide distance LH is a length L40 of the linear portion of the outerperipheral face 40 a of thefirst engagement portion 40 as viewed in the longitudinal sectional view. Further, Din represents the pitch diameter (effective diameter) of the belt at the drive pulley PLYDR, t represents the thickness of each element 24 (24′), and Nin represents the rotation speed of the drive pulley PLYDR. Note that unit of the rotation speed Nin is rpm, for example. Thus, “((Din×π/t)×(Nin/60))×2” represents the number of times therecess 36 and theprojection 38 slide on each other per second, that is, the number times therecess 36 and theprojection 38 contact each other per second. - As is known from the equation (1) above, the shorter the slide distance LH, the smaller the power loss LSSBLT. In view of this, since the linear portion length L40 shown in
FIG. 8B , which corresponds to the slide distance LH as described above, is shorter than the linear portion length L24′ shown inFIG. 8A , it is considered that the power losses caused by therecess 36 and theprojection 38 sliding (slipping) on each other at the drive pulley belt leaving position P01, the drive pulley belt entering position P02, the driven pulley belt entering position P03, and the driven pulley belt leaving position P04 (refer toFIG. 3 ) are smaller in the example embodiment shown inFIG. 8B than in the comparative example shown inFIG. 8A . - According to the example embodiment, each
element 24 has the ring-fit groove 30 in which thering 22 is fit, and the width of the slot gap CLCSLT between the radially outer sideinner face 50 of the ring-fit groove 30 and the outerperipheral face 52 of thering 22, as measured in the radial directions of thepulleys inner face 46 of the ring-fit groove 30 and the innerperipheral face 48 of thering 22 are in contact with each other, is larger than the width of the radial engagement gap CLC1 (=DH−DN). Eachelement 24 is moved toward the radially outer side of the drivepower transfer belt 10 by therecess 36 of the precedingadjacent element 24 and therings 22 at the moment theelement 24 leaves eachpulley element 24 passes though the drive pulley belt leaving position P01 and the driven pulley belt leaving position P04 (refer toFIG. 3 ). According to the above-described structure of the example embodiment, the work of therecess 36 of the precedingadjacent element 24 in the above state is large, and therefore the pressing force that theelement 24 applies, when moved toward the radially outer side of the drivepower transfer belt 10, to therings 22 is small, resulting in longer lives of therings 22, that is, a longer life of the drivepower transfer belt 10. In the following, how eachelement 24 is moved toward the radially outer side of the drivepower transfer belt 10 at the drive pulley belt leaving position P01 and at the driven pulley belt leaving position P04 will be described in more detail with reference toFIG. 9 . -
FIG. 9 is an enlarged view of therecess 36, thering 22, and their peripheries at the drive pulley belt leaving position P01 or at the driven pulley belt leaving position P04, and it illustrates, by way of example, how eachelement 24 is moved toward the radially outer side of the drivepower transfer belt 10 at the drive pulley belt leaving position P01 and at the driven pulley belt leaving position P04. Although it appears inFIG. 9 that thering 22 has a five-layer structure, this is only for simplifying the illustration, and it does not show the number of the actual layers of eachring 22.FIG. 9 is a longitudinal sectional view showing therecess 36 and theprojection 38, as areFIGS. 7A and 7B . The side where theprojections 38 of therespective elements 24 are present corresponds to the side where the belt-released section is present, while the side where therecesses 36 of therespective elements 24 are present corresponds to the side where the belt-riding section is present. For facilitating understanding on the descriptions, inFIG. 9 , theelements 24 are denoted “theelement 24A”, “theelement 24B”, and “theelement 24C” in this order from the belt-released section side. In the state illustrated inFIG. 9 , the radially outer sideinner face 50 of the ring-fit groove 30 of theelement 24B starts to contact, from thesecond face 34 side, the outerperipheral face 52 of each ring 22 (refer to the area P07) and therefore theelement 24B is lifted up by therings 22 toward the radially outer side of the drivepower transfer belt 10, as indicated by the arrow ARELB, as the drivepower transfer belt 10 runs. Then, as a result of theelement 24B lifted up to the radially outer side of the drivepower transfer belt 10, theprojection 38 of theelement 24C and therecess 36 of theelement 24B contact each other in the area P08 that is the engagement section between therecess 36 and theprojection 38 at the side corresponding to the radially inner side of the drivepower transfer belt 10, so that therecess 36 of theelement 24B lifts theelement 24C up toward the radially outer side of the drivepower transfer belt 10 as the drive power transfer belt further runs. Then, when the radially outer sideinner face 50 of each ring-fit groove 30 of theelement 24C starts to contact the outerperipheral face 52 of thecorresponding ring 22, theelement 24C is lifted up by therings 22 toward the radially outer side of the drivepower transfer belt 10, as has been theelement 24B. As mentioned earlier, in theelements 24 of the example embodiment, the slot gap CLCSLT (refer to the area P09 shown inFIG. 9 ) is larger than the radial engagement gap CLC1. However, if the slot gap CLCSLT of theelements 24 was smaller than the radial engagement gap CLC1, the radially outer sideinner face 50 of each ring-fit groove 30 would contact the outerperipheral face 52 of thecorresponding ring 22 at theelement 24C before therecess 36 of theelement 24B contacts theprojection 38 of theelement 24C in the area P08, causing an increase in the compressive stress, that is, the pressing force occurring in the thickness direction of the rings 22 (i.e., the direction in which the thickness of eachring 22 is measured) when theelement 24C is lifted up toward the radially outer side of the drivepower transfer belt 10. With theelements 24 of the example embodiment, as such, it is possible to reduce the pressing force that eachelement 24 applies to therings 22 when it is moved toward the radially outer side of the drivepower transfer belt 10 at the drive pulley belt leaving position P01 and at the driven pulley belt leaving position P04, resulting in a longer life of the drivepower transfer belt 10. - According to the example embodiment, further, the height of the
first engagement portion 40 from thesecond face 34 of theprojection 38 is preferably within the range of 0.25 to 0.4 mm. In this case, undesirable behaviors and motions of eachelement 24 in the belt-released sections can be more effectively suppressed, and further, as described above with reference toFIGS. 8A and 8B , the distance over which the outer peripheral face of theprojection 38 and the inner peripheral face of therecess 36 rub against each other when theprojection 38 and therecess 36 slide on each other in the longitudinal direction of the drivepower transfer belt 10 at the drive pulley belt leaving position P01, the drive pulley belt entering position P02, the driven pulley belt entering position P03, and the driven pulley belt leaving position P04 (refer toFIG. 3 ) is reduced, resulting in a smaller power loss that is caused by the outer peripheral face of theprojection 38 and the inner peripheral face of therecess 36 rubbing against each other. - While the invention has been explained in conjunction with the specific exemplary embodiment thereof, it is evident that many alternatives, modifications, and variations will be apparent to those skilled in the art. Accordingly, the example embodiment of the invention as set forth herein is intended to be illustrative, not limiting.
- For example, while the drive
power transfer belt 10 has the twoparallel rings 22 in the foregoing example embodiment as shown inFIG. 2 , the number of the rings is not limited to two. That is, the drive power transfer belt may have a single ring or three or more rings. - Further, while it has been mentioned, by way of example, that the
elements 24 in the foregoing example embodiment may be manufactured by pressing, the elements may be manufactured by various other methods, such as die-casting. - While the outer
peripheral face 42 a of thesecond engagement portion 42 of theprojection 38 of eachelement 24 in the forgoing example embodiment is tapered over its entire circumference as shown inFIGS. 6A , 6B, and 6C, the entire circumferential face of the outerperipheral face 42 a is not necessarily inclined by being tapered, for example. That is, for example, it is sufficient that aninclined face 60 that is larger in the gradient with respect to the axis of theprojection 38 than that of thefirst engagement portion 40 be provided at least at a portion, at the side corresponding to the radially outer side of the drivepower transfer belt 10, of the second engagement portion 42 (refer toFIGS. 10A , 10B, 10C, 11A, 11B, and 11C) as follows. For example, eachelement 24 may have, in place of theprojection 38, aprojection 62 shown inFIGS. 10A , 10B, and 10C as the first modification example of the foregoing example embodiment, or aprojection 72 shown inFIGS. 11A , 11B, and 11C as the second modification example of the foregoing example embodiment.FIGS. 10A , 10B, and 10C are views for illustrating the detailed form of theprojection 62 in the first modification example of the example embodiment, which replaces theprojection 38 of theelement 24. More specifically,FIG. 10A is an enlarged view of theprojection 62 and its periphery,FIG. 10B is a sectional view of theprojection 62 taken along the line indicated by the arrows B2 inFIGS. 10A , andFIG. 10C is a sectional view of theprojection 62 taken along the line indicated by the arrows C2 inFIG. 10A , which is orthogonal to the line indicated by the arrows B2. Although theprojection 62 shown inFIGS. 10A , 10B, and 10C is basically the same as theprojection 38 described above, theprojection 62 is different from theprojection 38 in that the outer peripheral face of asecond engagement portion 64 provided at the tip side of theprojection 62 is basically tapered at an angle equal to the tapering angle of the outerperipheral face 40 a of thefirst engagement portion 40 described above, and a portion, at the side corresponding to the radially outer side of the drivepower transfer belt 10, of thesecond engagement portion 64 of theprojection 62 is chamfered so as to form an inclined face (radially outer side inclined face) 60 that is larger in the gradient with respect to the axis of theprojection 62 than that of thefirst engagement portion 40. For example, the gradient of the radially outer side inclinedface 60 with respect to the axis of theprojection 62 is, for example, equal to the gradient of the outerperipheral face 42 a of thesecond engagement portion 42 shown inFIG. 6C . - Next,
FIGS. 11A , 11B, and 11C are views for illustrating the detailed form of theprojection 72 in the second modification example of the example embodiment, which replaces theprojections FIG. 11A is an enlarged view of theprojection 72 and its periphery,FIG. 11B is a sectional view of theprojection 72 taken along the line indicated by the arrows B3 inFIG. 11A , andFIG. 11C is a sectional view of theprojection 72 taken along the line indicated by the arrows C3 inFIG. 11A , which is orthogonal to the line indicated by the arrows B3. Although theprojection 72 shown inFIGS. 11A , 11B, and 11C is basically the same as theprojection 38 described above, theprojection 72 is different from theprojection 38 in that the outer peripheral face of asecond engagement portion 74 provided at the tip side of theprojection 72 is basically tapered at an angle equal to the tapering angle of the outerperipheral face 40 a of thefirst engagement portion 40 described above, as in the case of theprojection 62 shown inFIGS. 10A , 10B, and 10C, and a portion, at the side corresponding to the radially outer side of the drivepower transfer belt 10, of thesecond engagement portion 74 and a portion, at the side corresponding to the radially inner side of the drivepower transfer belt 10, of thesecond engagement portion 74 are both chamfered so as to form, at the side corresponding to the radially outer side of the drivepower transfer belt 10, a radially outer side inclinedface 60 that is the same as the radially outer side inclinedface 60 of theprojection 62 shown inFIGS. 10A , 10B, and 10C and to form, at the side corresponding to the radially inner side of the drivepower transfer belt 10, a radially inner side inclinedface 76 of which form is symmetrical, about the axis of theprojection 72, to the form of the radially outer side inclinedface 60. - As shown in
FIGS. 6A , 6B, 6C, 10A, 10B, 10C, 11A, 11B, and 11C, thesecond engagement portion 42 of theprojection 38, thesecond engagement portion 64 of theprojection 62, and thesecond engagement portion 74 of theprojection 72 have, respectively, the inclined faces 42 a and 60 that are each provided at least at the side corresponding to the radially outer side of the drivepower transfer belt 10 and are larger in the gradient with respect to the axes of therespective projections first engagement portion 40. Therefore, the gap between the tip side of theprojection 38 and therecess 36, the gap between the tip side of theprojection 62 and therecess 36, and the gap between the tip side of theprojection 72 and therecess 36 are sufficiently large at the side corresponding to the radially outer side of the drivepower transfer belt 10. As such, when theadjacent elements 24 incline relative to each other at a certain angle, as viewed in the axial direction of thepulleys respective pulleys projection recess 36 into which the same projection fits. Further, the distance (slide distance) over which therecess 36 and theprojection 38 shown inFIGS. 6A , 6B, and 6C rub against each other at the drive pulley belt leaving position P01, the drive pulley belt entering position P02, the driven pulley belt entering position P03, and the driven pulley belt leaving position P04 (refer toFIG. 3 ), which has been described earlier with reference toFIGS. 8A and 8B , does not change even if theprojection 62 shown inFIGS. 10A , 10B, and 10C or theprojection 72 shown inFIGS. 11A , 11B, and 11C is provided in place of theprojection 38. That is, even in a case where theprojection 38 shown inFIGS. 6A , 6B, and 6C is replaced with theprojection 62 or theprojection 72, the same power loss reduction effect as theprojection 38 shown inFIGS. 6A , 6B, and 6C can be obtained. - According to the structure of the example embodiment shown in
FIGS. 6A , 6B, and 6C, the outerperipheral face 42 a of thesecond engagement portion 42 of theprojection 38 is tapered. However, as the third modification example of the foregoing example embodiment, aprojection 82 shown inFIGS. 12A , 12B, and 12C may be provided in place of theprojection 38 shown inFIGS. 6A , 6B, and 6C. Theprojection 82 has asecond engagement portion 84, and thesecond engagement portion 84 has an outerperipheral face 84 a that is formed by rounding the peripheral edge of atop face 86 of theprojection 82 at a curvature radius of 0.4 to 0.5 mm.FIGS. 12A , 12B, and 12C are views for illustrating the detailed form of theprojection 82 of the third modification example of the example embodiment, which replaces theprojections FIG. 12A is an enlarged view of theprojection 82 and its periphery,FIG. 12B is a sectional view of theprojection 82 taken along the line indicated by the arrows B4 inFIG. 12A , andFIG. 12C is a sectional view of theprojection 82 taken along the line indicated by the arrows C4 inFIG. 12A , which is orthogonal to the line indicated by the arrows B4. Although theprojection 82 shown inFIGS. 12A , 12B, and 12C is basically the same as theprojection 38 described above, theprojection 82 is different from theprojection 38 in that the outerperipheral face 84 a of thesecond engagement portion 84 provided at the tip side of theprojection 82 is formed by rounding the peripheral edge of atop face 86 of theprojection 82 at a curvature radius of 0.4 to 0.5 mm, rather than being tapered. The numerical range of 0.4 to 0.5 mm for the curvature radius has been empirically set as a numerical range that ensures that thefirst engagement portion 40 of theprojection 38 and therecess 36 engage enough to suppress undesirable behaviors and motions of theelements 24 when they are stacked on each other in either of the belt-released sections described above, and that minimizes the power loss caused by the outerperipheral face 40 a of thefirst engagement portion 40 and the inner peripheral face of therecess 36 rubbing against each other at the drive pulley belt leaving position P01, the drive pulley belt entering position P02, the driven pulley belt entering position P03, and the driven pulley belt leaving position P04 (refer toFIG. 3 ). Referring toFIGS. 12A , 12B, and 12C, since the outerperipheral face 84 a of thesecond engagement portion 84 of theprojection 82 is formed by rounding the peripheral edge of thetop face 86 of theprojection 82 at a curvature radius of 0.4 to 0.5 mm, undesirable behaviors and motions of theelements 24 can be more properly suppressed at each belt-released section. Further, as in the case described above with reference toFIGS. 8A and 8B , the distance over which the outer peripheral face of theprojection 82 and the inner peripheral face of therecess 36 rub against each other when theprojection 82 and therecess 36 slide on each other in the longitudinal direction of the drivepower transfer belt 10 at the drive pulley belt leaving position P01, the drive pulley belt entering position. P02, the driven pulley belt entering position P03, and the driven pulley belt leaving position P04 (refer toFIG. 3 ) is reduced, resulting in a smaller power loss that is caused by the outer peripheral face of theprojection 82 and the inner peripheral face of therecess 36 rubbing against each other. It is to be noted that thesecond engagement portion 84 of theprojection 82 shown inFIGS. 12A , 12B, and 12C may additionally have the radially outer side inclinedface 60 shown inFIGS. 10A , 10B, and 10C or the radially outer side inclinedface 60 and the radially inner side inclinedface 76 shown inFIGS. 11A , 11B, and 11C. - Meanwhile, as described above, the diameter of the
projection 38 of the foregoing example embodiment decreases toward to the tip of theprojection 38 from thesecond face 34 as shown inFIGS. 6A , 6B, and 6C. With regard to this structural feature, preferably, theprojection 38 is located on the inner side (the side indicated by the arrow ARIN inFIG. 6C ) of an arc ARC1 that is drawn about the rocking center about which theelement 24 having thesame projection 38 rocks relative to theelements 24 adjacent to it, as viewed in the axial direction of thepulleys edge portion 28 shown inFIG. 6C , such that the arc ARC1 runs through a position PT01 at the base of theprojection 38, which is most distant from the rocking center (i.e., the rocking edge portion 28). According to this structure, for example, when theprojection 38 slides, in the longitudinal direction of the drivepower transfer belt 10, into therecess 36 mating with it as theelement 24 having thesame projection 38 rocks about the rockingedge portion 28 thereof (i.e., the rocking center) at the drive pulley belt leaving position P01, the drive pulley belt entering position P02, the driven pulley belt entering position P03, and the driven pulley belt leaving position P04 (refer toFIG. 3 ), the intensity of rubbing between the outer peripheral face of theprojection 38 and the inner peripheral face of therecess 36 is small, resulting in a decrease in the power loss that is caused by such rubbing. - In the meantime, it is to be understood that although not described herein, there are various other modifications and changes that may be made without departing from the spirit and scope of the invention.
- While the invention has been described with reference to example embodiments thereof, it is to be understood that the invention is not limited to the described example embodiments or constructions. To the contrary, the invention is intended to cover various modifications and equivalent arrangements. In addition, while the various elements of the example embodiments are shown in various combinations and configurations, other combinations and configurations, including more, less or only a single element, are also within the scope of the invention.
Claims (6)
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
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JP2011-029345 | 2011-02-15 | ||
JP2011029345A JP5302992B2 (en) | 2011-02-15 | 2011-02-15 | Element of transmission belt in belt type continuously variable transmission for vehicle |
Publications (2)
Publication Number | Publication Date |
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US20120208663A1 true US20120208663A1 (en) | 2012-08-16 |
US9109655B2 US9109655B2 (en) | 2015-08-18 |
Family
ID=46637327
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
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US13/372,965 Expired - Fee Related US9109655B2 (en) | 2011-02-15 | 2012-02-14 | Elements of drive power transfer belt of belt-drive continuously variable transmission for vehicle |
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Country | Link |
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US (1) | US9109655B2 (en) |
JP (1) | JP5302992B2 (en) |
CN (1) | CN102691750B (en) |
Cited By (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US20130040772A1 (en) * | 2010-04-28 | 2013-02-14 | Toyota Jidosha Kabushiki Kaisha | Power transmission belt and method of producing the same |
US9279475B2 (en) * | 2012-07-06 | 2016-03-08 | Honda Motor Co., Ltd. | Element for metallic belt |
US20210172496A1 (en) * | 2019-12-10 | 2021-06-10 | Robert Bosch Gmbh | Transverse segment for a drive belt and a drive belt for a continuously variable transmission including the transverse segment and a ring stack |
US11391343B2 (en) * | 2019-02-12 | 2022-07-19 | Toyota Jidosha Kabushiki Kaisha | Continuously variable transmission |
Families Citing this family (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
NL1039973C2 (en) * | 2012-12-24 | 2014-06-25 | Bosch Gmbh Robert | Drive belt with a carrier ring and transverse segments. |
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US11486464B2 (en) * | 2019-12-10 | 2022-11-01 | Robert Bosch Gmbh | Transverse segment for a drive belt and a drive belt for a continuously variable transmission including the transverse segment and a ring stack |
Also Published As
Publication number | Publication date |
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CN102691750A (en) | 2012-09-26 |
JP2012167741A (en) | 2012-09-06 |
US9109655B2 (en) | 2015-08-18 |
JP5302992B2 (en) | 2013-10-02 |
CN102691750B (en) | 2014-07-16 |
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